US4765288A - Valve control arrangement - Google Patents

Valve control arrangement Download PDF

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Publication number
US4765288A
US4765288A US06/875,318 US87531886A US4765288A US 4765288 A US4765288 A US 4765288A US 87531886 A US87531886 A US 87531886A US 4765288 A US4765288 A US 4765288A
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United States
Prior art keywords
valve
opening
stroke
return spring
transmitting chamber
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Expired - Fee Related
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US06/875,318
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English (en)
Inventor
Ernst Linder
Helmut Rembold
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Robert Bosch GmbH
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Robert Bosch GmbH
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Assigned to ROBERT BOSCH GMBH, 7000 STUTTGART 1, GERMANY reassignment ROBERT BOSCH GMBH, 7000 STUTTGART 1, GERMANY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: LINDER, ERNST, REMBOLD, HELMUT
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0031Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of tappet or pushrod length
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423Details relating to the hydraulic feeding circuit
    • F01L2001/34446Fluid accumulators for the feeding circuit

Definitions

  • the present invention relates to a valve control arrangement. More particularly, it relates to a valve control arrangement for controlling closing and opening time of a valve in a displacement piston-internal combustion engine, the valve actuatable by a valve control cam of a cam shaft via an axially displaceable valve plunger.
  • Valve control arrangements of the above mentioned general type are known in the art.
  • One of the valve control arrangements is disclosed in the German document DE-OS No. 3,125,650 and designed so that at the beginning of the stroke of the valve control cam which acts for valve opening, the opening of the stroke transmitting chamber is blocked.
  • the pressure of the valve control cam upon the stroke transmitting chamber, on which also the valve plunger abuts under the force of the valve closing spring in an opposite direction no pressure medium can discharge from the stroke transmitting chamber.
  • the stroke movement of the valve control cam which is produced by the rotary movement of the cam shaft is completely transmitted to the valve plunger which in turn lifts the valve member from the valve seat and opens the valve.
  • the closing of the valve is performed at a predetermined point of time so that the opening of the stroke transmitting chamber is performed in a shock-like manner.
  • the pressure medium flows out of the pressure transmitting chamber and therefore its axial extension reduces.
  • the valve plunger can move under the action of the valve closing spring in direction toward the valve control cam, and thereby close the valve.
  • the stroke of the valve plunger or the valve member is shown in FIG. 2 vs the rotary angle of the valve control cam.
  • the curve I represents the course with closed opening of the stroke transmitting chamber
  • the curve II represents the course with release of the opening of the stroke transmitting chamber at point of time ⁇ SII .
  • the quantity of fuel aspirated into the cylinder can be adjusted in correspondence with different consumption in different operational conditions.
  • valve control arrangement which is designed so that at the beginning of the stroke of the valve control cam which acts for valve opening, the controllable opening of the stroke transmitting chamber is adjusted to an unloading cross-section so that to the closing point of time of the valve a partial quantity of pressure medium can flow out of the stroke transmitting chamber.
  • valve control arrangement When the valve control arrangement is designed in accordance with the present invention, it has the disadvantage that with the same fuel quantity flowing into the cylinder, the valve opening time is considerably increased and thereby the evacuating stroke in the cylinder after closing of the valve is considerably reduced.
  • the above-described problems with the fuel cooling and poor mixture preparation are essentially improved and the hydrocarbon content in waste gas is considerably reduced. Since a smaller inner cross-section is available for the fuel mixture quantity during longer valve opening time, the flow speed is increased and thereby the mixture preparation is improved also during idle running and in the lower partial load region.
  • the longer valve opening time for fuel mixture filling is obtained by the unloading cross-section in the opening of the stroke transmitting chamber, adjustable with the beginning of the valve opening stroke. Thereby a partial quantity of the pressure medium can flow out during the cam stroke of the valve control cam acting for the valve opening.
  • the finally adjusted dynamic pressure in the stroke transmitting chamber is sufficient to open the valve with the desired opening course along the rotary angle ⁇ SII , as can be seen in FIG. 2 on the curve III.
  • a change-over switch for converting the electromagnets from partial to full excitement, and it is controlled in dependence on a load signal obtained advantageously on the drive pedal of a vehicle and on the motor rotary speed.
  • the limitation to the operational region of the internal combustion engine is advantageous since here a maximum reduction of the hydrocarbon waste gas can be obtained.
  • the fuel preparation also during short valve opening time or longer evacuating phase is so good that the hydrocarbon content in fuel is increased only insigificantly.
  • increased throttle losses are taken into account with constant fuel mixture filling because of the reduced inlet cross-section of the valve.
  • the point of time of closing of the valve is corrected in dependence on the running quietness of the internal combustion engine.
  • FIG. 1 is a view showing a longitudinal section of a valve control arrangement for an inlet valve of displacement piston-internal combustion engine
  • FIG. 2 is a diagram of an inlet valve-stroke in dependence on the rotary angle of a valve control cam
  • FIG. 3 is a view showing a longitudinal section of a magnetic valve of the valve control arrangement of FIG. 1 in connection with a block diagram of a magnetic valve control;
  • FIG. 4 is a diagram of the spring force versus the valve needle stroke in the magnetic valve of FIG. 3.
  • a valve control arrangement for an inlet valve 10 of an internal combustion engine, here a combustion motor, is arranged between a valve plunger 12 which carries a valve member 11, and a valve cam 14 rotatable on a cam shaft 13.
  • the valve plunger 12 is axially displaceably guided in a valve housing 15, and sits with the valve member 11 on a valve seat 18 in the valve housing 15 under the action of two valve closing springs 16 and 17.
  • a valve inlet opening 19 is formed in the valve housing 15.
  • the valve control arrangement has a housing 20 which is arranged on the valve housing 15.
  • a housing chamber 21 is formed in the housing 20 so that it is in alignment with a spring chamber 22 in the valve housing 15 which accommodates the coaxial valve closing springs 16 and 17.
  • a housing block 23 is inserted from below into the housing chamber 21 and has a central axially throughgoing housing opening 24.
  • a valve piston 25 and a piston part 26 of a cam piston 27 are axially displaceable in the housing opening 24.
  • the cam piston 27 is pressed against the valve control cam 14 by a return spring 28 which is supported on the housing block 23.
  • the piston part 26 is either fixedly connected with the cup-shaped cam piston 27 or retained in abutment against the cam piston 27 via the same return spring 28.
  • the valve piston 25 and the piston part 26 limit a stroke transmitting chamber 29 which is filled with a pressure medium, here oil.
  • the effective axial length of the stroke transmitting chamber 29 between the cam piston 27 and the piston part 26 can be changed by relative movement of the pistons relative to one another.
  • the stroke transmitting chamber 29 communicates via conduits 30, on the one hand, with a spring accumulator 31 and, on the other hand, with a supply container 32.
  • a check valve 33 and a filling pump 34 are arranged between the conduit 30 and the supply container 32.
  • the conduit 30 permits displacement of the oil volumes available in the stroke transmitting chamber 29 into the spring accumulator 31 and vice versa. Leakage losses in oil volumes are compensated by the feeding pump 34 and the check valve 33 from the supply container 32.
  • a magnetic valve 35 is arranged in the conduit 30.
  • the magnetic valve 35 is reached by a bypass conduit 36.
  • a check valve 37 is arranged in the bypass conduit 36 so that the oil can flow from the spring accumulator 31 with bypassing of the magnetic valve 35, into the stroke transmitting chamber 29.
  • the magnetic valve 35 is shown in a longitudinal section in FIG. 3.
  • the magnetic valve 35 is connected with its valve inlet 38 to the conduit portion connected with the stroke transmitting chamber 29, and with its valve outlet 39 with the conduit portion connected with the spring accumulator 31, the conduit portion being connected to a portion of the conduit 30.
  • the valve inlet 38 and the valve outlet 39 are connected by a throughflow conduit 40 which inner cross-section is controlled by a valve needle 41.
  • the valve needle 41 is connected with an armature 42 of an electromagnet 43 and guided displaceably in an axial opening 44.
  • a return spring 46 engages an annular flange 45 which is formed of one-piece with the valve needle 41.
  • the return spring 46 holds the valve needle 41 in the valve opening position in condition of not energized electromagnet 43.
  • the spring characteristic of the return spring 46 which provides a small tensioning is shown in FIG. 4 as a curve a.
  • the end of the valve needle 41 which faces toward the throughflow opening 40 has a recess 47.
  • a bush 49 is displaceable on a guiding rod 48 and extends into the recess 47.
  • the bush 49 is supported on an abutment 51 under the action of a second return spring 50.
  • the abutment 51 is arranged so that the valve needle 41 must cover a displacement path s 1 before the bottom of the recess 47 comes into contact with the bush 49.
  • the total stroke of the valve needle 41 from its opening position in condition of not energized electromagnet 43 to its closing position in which its end side is pressed against a valve seat 52 which surrounds the throughflow opening 40 is identified in FIGS. 3 and 4 with s ges .
  • the spring characteristic of the second return spring 50 is identified in FIG. 4 with reference letter b, the second return spring 50 is also pretensioned. However, its tensioning force, as can be seen in FIG. 4, is considerably higher than the tensioning force of the first return spring 46.
  • An exciting winding 53 of the electromagnet 43 is connected with a changeover switch 54.
  • the changeover switch 54 has three switching positions. In both outer switching positions the exciting winding 53 is connected with a direct current source 55, and because of differently dimensioned resistors 56, 57 the electromagnet 43 can be once fully excited and once partially excited.
  • the partial excitation is selected so that the valve needle 41 can cover the displacement path s 1 against the force of the first return spring 46, but cannot overcome the spring force of the second return spring 50.
  • the full excitation is selected so that the valve needle 41 can cover the total stroke s ges against return force of both return springs 46, 50.
  • the magnet valve 35 is formed pressure equalized, in other words, in the event of pressure increase or pressure decrease at both sides of the throughflow opening 40, no additional valve closing forces or valve opening forces act upon the valve needle 41.
  • This pressure equalization is obtained statically by equal diameter of the valve needle 41 on the valve seat 52, on the one hand, and on the sealing edge 63 which seals the valve needle 41 in the axial opening 44, on the other hand. Dynamically it is obtained by a respective geometry of the valve seat 52 and the part of the valve needle 41 which cooperates with the valve seat.
  • the point of time of turning on of the electromagnet 43 as well as of the turning on of the partial or full excitation of the electromagnet 43 is controlled by a control device 58 which provides, in dependence on two control signals, full or partial excitation of the electromagnet 43.
  • the control device 58 operates so that in idle running and in lower partial load region the partial excitation is obtained, and with full load or in upper partial load region the full excitation of the electromagnet 43 is obtained at the point of time of the turning on.
  • the control signals are produced by two sensors 59 and 60.
  • the load sensor 59 determines the position of a drive pedal 61, while the rotary speed sensor 60 determines the rotary speed of the internal combustion engine.
  • the point of time of the turning on of the partial or full excitation is adjusted in dependence upon the rotary position of the valve control cam 14, while the point of time of the turning off is controlled in dependence upon the required fuel mixture-filling quantity.
  • a control signal for correcting the point of time of turning-on is supplied to the control device 58. This control signal is produced from the rotary speed of the internal combustion engine determined by a known smooth running measuring device 62, and from the comparison of the nominal and actual values.
  • valve control arrangement operates in the following manner:
  • the cam piston 27 moves downwardly.
  • the changeover switch 54 is controlled by the control device and the exciting winding 53 is connected with the direct current source 55. If the motor is in the full load or upper partial load region, the magnetic valve 35 is excited fully and transfers by closing of the throughflow opening 40 by the valve needle 41 to its blocking position. The stroke transmitting chamber 29 is thereby blocked, so that with the introduced axial displacement of the piston part 26 of the cam piston 27 no oil can discharge from the stroke transmitting chamber 29.
  • the stroke movement of the cam piston 27 is transmitted thereby via the oil cushion available in the stroke transmitting chamber 29 to the valve piston 25. The latter performs the same stroke path as the piston part 26.
  • the stroke movement of the valve piston 25 causes an identical stroke movement of the valve plunger 12 and thereby the valve member 11 of the inlet valve 10.
  • the stroke of the inlet valve 10 is shown in FIG. 2 by curves I and II.
  • the curve I corresponds to the inlet valve stroke for the case when the stroke transmitting chamber 29 remains closed during the entire cam stroke of the valve control cam 14. With the open inlet valve, or in other words, the valve member 11 lifted from the valve seat 18, the fuel mixture flows into a not shown cylinder of the combustion motor.
  • the closing process of the inlet valve 10 is started by turning off of the magnet excitation of the magnetic valve 35, in correspondence with the desired fuel mixture-filling quantity in point of time ⁇ SII , or in other words, in the point of time in which the valve control cam 14 has been rotated by the rotary angle ⁇ SII .
  • This is provided by a respective control signal of a control device 58 to the changeover switch 54.
  • the magnet valve 35 opens since the valve needle 41 is transferred by both return springs 46, 50 to its open position.
  • the valve piston 25 can move upwardly under the action of both valve closing springs 16, 17 of the inlet valve 10, with expelling of oil from the stroke transmitting chamber 29 through the open throughflow opening 40.
  • the valve member 11 is seated on the valve seat 18 and the inlet valve 10 is closed.
  • the stroke of the inlet valve is shown in FIG. 2 by the curve II.
  • Control signals are supplied to the control device 58 via the sensors 59, 60 and indicate the operational condition idling running or lower load region.
  • the changeover switch 54 is switched so that the electromagnet 43 of the magnetic valve 35 is excited only partially. This partial excitation is selected so that the valve needle 41 covers only the displacement path s 1 and thereby provides a reduced cross-section of the throughflow opening 40.
  • the axial length of the stroke transmitting chamber 29 effective between the piston part 26 and the cam piston 27 reduces.
  • the finally adjusted dynamic pressure causes a displacement of the valve piston 25 and thereby a displacement of the valve plunger 12 and a displacement of the valve member 11 whose course is characterized by the curve III in FIG. 2.
  • the opening movement of the inlet valve takes place much slower.
  • a fuel mixture flows into the cylinder of the motor and is determined in correspondence with the operational conditions.
  • the control device 58 provides in the point of time ⁇ SIII a turning off signal to the changeover switch 54, so that the magnetic valve 35 is turned off as described hereinabove and the inlet valve 10 closes as described hereinabove.
  • a curve III' for the stroke of the inlet valve is identified for comparison in FIG. 2 in dotted line, and during this stroke the opening cross-section of the inlet valve 10 in time is identical with the inlet cross-section in time for a stroke course in accordance with curve III.
  • the second return spring 50 can be dispensed with when the stroke of the electromagnet 43 and thereby the displacement of the valve needle 41 is adjustable in a stepless manner via the exciting current for the exciting winding 53 of the electromagnet 43.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
US06/875,318 1985-09-12 1986-06-16 Valve control arrangement Expired - Fee Related US4765288A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3532549 1985-09-12
DE19853532549 DE3532549A1 (de) 1985-09-12 1985-09-12 Ventilsteuervorrichtung

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JP (1) JPS6263107A (nl)
DE (1) DE3532549A1 (nl)

Cited By (29)

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US4873949A (en) * 1987-11-19 1989-10-17 Honda Giken Kogyo Kabushiki Kaisha Method of and apparatus for controlling valve operation in an internal combustion engine
US4889084A (en) * 1988-05-07 1989-12-26 Robert Bosch Gmbh Valve control device with magnetic valve for internal combustion engines
US4889085A (en) * 1987-11-19 1989-12-26 Honda Giken Kogyo Kabushiki Kaisha Valve operating device for internal combustion engine
US4977867A (en) * 1989-08-28 1990-12-18 Rhoads Jack L Self-adjusting variable duration hydraulic lifter
US4982706A (en) * 1989-09-01 1991-01-08 Robert Bosch Gmbh Valve control apparatus having a magnet valve for internal combustion engines
WO1991003627A1 (de) * 1989-09-01 1991-03-21 Robert Bosch Gmbh Ventilsteuervorrichtung mit magnetventil für brennkraftmaschinen
US5002022A (en) * 1989-08-30 1991-03-26 Cummins Engine Company, Inc. Valve control system with a variable timing hydraulic link
WO1991005146A1 (en) * 1989-10-03 1991-04-18 Siemens Aktiengesellschaft Solenoid control of engine valves with accumulator pressure recovery
WO1991008380A1 (de) * 1989-11-25 1991-06-13 Robert Bosch Gmbh Hydraulische ventilsteuervorrichtung für eine mehrzylinder-brennkraftmaschine
US5080055A (en) * 1989-04-13 1992-01-14 Nissan Motor Company, Ltd. Variable valve timing arrangement for internal combustion engine
US5103779A (en) * 1989-04-18 1992-04-14 Hare Sr Nicholas S Electro-rheological valve control mechanism
US5140955A (en) * 1990-03-08 1992-08-25 Giken Kogyo K.K. (Honda Motor Co., Ltd., in English) Method of controlling an internal combustion engine
US5140953A (en) * 1991-01-15 1992-08-25 Fogelberg Henrik C Dual displacement and expansion charge limited regenerative cam engine
US5247913A (en) * 1992-11-30 1993-09-28 John Manolis Variable valve for internal combustion engine
US5263441A (en) * 1989-11-25 1993-11-23 Robert Bosch Gmbh Hydraulic valve control apparatus for internal combustion engines
US5526784A (en) * 1994-08-04 1996-06-18 Caterpillar Inc. Simultaneous exhaust valve opening braking system
US5540201A (en) * 1994-07-29 1996-07-30 Caterpillar Inc. Engine compression braking apparatus and method
US5647318A (en) * 1994-07-29 1997-07-15 Caterpillar Inc. Engine compression braking apparatus and method
US5931125A (en) * 1994-06-02 1999-08-03 Valasopoulos; Christos Piston internal combustion engine variable action valve lifter system
EP0972972A3 (de) * 1998-07-14 2001-09-19 Bayerische Motoren Werke Aktiengesellschaft Betriebsverfahren für eine Fahrzeug-Brennkraftmaschine
US6321701B1 (en) * 1997-11-04 2001-11-27 Diesel Engine Retarders, Inc. Lost motion valve actuation system
EP1243762A3 (en) * 2001-03-23 2003-07-02 C.R.F. Società Consortile per Azioni Internal-combustion engine with hydraulic system for variable operation of the engine valves
US6622678B2 (en) * 2001-06-21 2003-09-23 Unisia Jecs Corporation Apparatus and method for controlling variable valve mechanism
US6814409B2 (en) 2001-04-12 2004-11-09 A-Dec, Inc. Hydraulic drive system
EP1508676A2 (en) * 2001-07-06 2005-02-23 C.R.F. Società Consortile per Azioni Multi-cylinder diesel engine with variably actuated valves
US20100168987A1 (en) * 2008-12-29 2010-07-01 De Cristoforo Ferdinando Internal-combustion engine with variable actuation of the intake valves and self-adaptive control of the air-fuel ratio with supervision of the control functions
US20110277712A1 (en) * 2008-09-26 2011-11-17 Schaeffler Technologies Gmbh & Co. Kg Electrohydraulic valve controller
US8646422B2 (en) * 2010-08-20 2014-02-11 Hyundai Motor Company Electro-hydraulic variable valve lift apparatus
WO2016044148A1 (en) * 2014-09-17 2016-03-24 Fca Us Llc Engine variable valve lift system having integrated hydraulic fluid retention

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DE3716947C1 (de) * 1987-05-20 1988-03-03 Bayerische Motoren Werke Ag Ladungswechsel-Verfahren fuer eine 4-Takt-Hubkolben-Brennkraftmaschine
US4858956A (en) * 1988-09-22 1989-08-22 Siemens-Bendix Automotive Electronics L.P. High pressure, fast response, pressure balanced, solenoid control valve
JPH086571B2 (ja) * 1989-09-08 1996-01-24 本田技研工業株式会社 内燃機関の動弁装置
US5193496A (en) * 1991-02-12 1993-03-16 Volkswagen Ag Variable action arrangement for a lift valve
IT1285853B1 (it) 1996-04-24 1998-06-24 Fiat Ricerche Motore a combustione interna con valvole ad azionamento variabile.

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Publication number Priority date Publication date Assignee Title
US2587538A (en) * 1946-02-13 1952-02-26 Seaman Henry Solenoid valve
US3829060A (en) * 1972-02-22 1974-08-13 Bosch Gmbh Robert Magnet valve
US3788597A (en) * 1972-05-31 1974-01-29 Yukon Kogyo Co Ltd Electromagnetic flow controlling valve
US4258671A (en) * 1978-03-13 1981-03-31 Toyota Jidosha Kogyo Kabushiki Kaisha Variable valve lift mechanism used in an internal combustion engine
US4206728A (en) * 1978-05-01 1980-06-10 General Motors Corporation Hydraulic valve actuator system
US4466390A (en) * 1981-09-09 1984-08-21 Robert Bosch Gmbh Electro-hydraulic valve control system for internal combustion engine valves
US4494495A (en) * 1982-01-12 1985-01-22 Toyota Jidosha Kabushiki Kaisha Variable valve-timing apparatus in an internal combustion engine
US4509467A (en) * 1982-11-09 1985-04-09 Aisin Seiki Kabushiki Kaisha Hydraulic lifter system for variable cylinder engines
JPS59229013A (ja) * 1983-06-09 1984-12-22 Nissan Motor Co Ltd 油圧式弁駆動装置

Cited By (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4889085A (en) * 1987-11-19 1989-12-26 Honda Giken Kogyo Kabushiki Kaisha Valve operating device for internal combustion engine
US4873949A (en) * 1987-11-19 1989-10-17 Honda Giken Kogyo Kabushiki Kaisha Method of and apparatus for controlling valve operation in an internal combustion engine
US4889084A (en) * 1988-05-07 1989-12-26 Robert Bosch Gmbh Valve control device with magnetic valve for internal combustion engines
US5080055A (en) * 1989-04-13 1992-01-14 Nissan Motor Company, Ltd. Variable valve timing arrangement for internal combustion engine
US5103779A (en) * 1989-04-18 1992-04-14 Hare Sr Nicholas S Electro-rheological valve control mechanism
US4977867A (en) * 1989-08-28 1990-12-18 Rhoads Jack L Self-adjusting variable duration hydraulic lifter
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DE3532549C2 (nl) 1992-11-26
DE3532549A1 (de) 1987-03-19
JPS6263107A (ja) 1987-03-19

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